Guide roll



Sept. 23, 1958 R. N. sABEE 2,853,295

GUDE ROLL Filed oct. 28, 1954 4 sheets-sheet V1 Sept. 23, 1958 I R. N. SABE GUIDE ROLL v4 Sheets-Sheet 2 Filed oct. 28, 1954 'BY' jm, @mg Mm R. N. SAB-EE Sept. 23, 1958 GUIDE ROLL 4 Sheets-Sheet 3 Filed Oct. 28, 1954 ,Xo-mw, UMS( United States Patent GUIDE ROLL Reinhardt N. Sabee, Appleton, Wis. Application ctober 28, 1954, Serial No.` 465,295

13 Claims. (Cl. 271-2.6)

The present invention relates generally to travelling webs, endless belts, and the like, and is particularly directed to an improved form of guide roll for maintaining such webs or belts in centered relation to their path of movement.

In many installations of generally hat flexible conveyors it is necessary that means be provided for maintaining the travelling web in position with respect to its normal path. For example, in paper making machines wherein a wet web of fibrous pulp is formed o-n a moving Fourdrinier wire and then carried between felts to press rolls, driers etc., it is important to the operating eftciency of the machine that both the wire and the felts be kept in a true path without any appreciable deviation therefrom. In order to achieve this in each instance there is generally provided a guide roll Which is disposed in trans- -verse relation to the upper or functional run of the travelling Wire or felt and in frictional engagement therewith. The guide roll is mounted for movement in the direction of travel of the sheet, so that the oblique position of the frictionally engaged roll ei'rects a lateral shifting of the Wire or felt. Consequently, whenever the wire or felt deviates from a position centrally of its normal path, the guide roll can be moved to cause a shifting of the felt or wire in a direction which is eective to cause the endless felt or wire to resume its normal position.

Various meanshave been devised heretofore for eecting a compensating movement of the guide rollin response to lateral shifting of a travelling web or the like. However, such means have generally been rather complicated and bulky and require an appreciable amount of space for installations. As a result there are many instances wherein it is desirable to use a guide roll, but the lack of space does not permit it. This is particularly true in paper machines where the space alo-ng the felts and wire is quite limited.

Then too, the known devices for adjusting guide rolls of the type described are prone to override the point of correction, with the result that the travelling web is constantly shifting in a lateral direction with respect to its line of travel. This hunting effect of the guide roll is, of course, undesirable in that it tends to shorten the useful life of the Fourdrinier wire, felts, and the like, and may produce wrinkles therein.

It is also noted that in the case of iluid operated devices for shifting a guide roll a failure of the fluid pressure permits the guide roll to shift its position abruptly and this frequently results in damage to the-travelling web.

It is the primary object of the present invention to provide a new and improved form of mechanism for adjusting the position of a guide roll. Another object is to provide means for positioning a guide roll, which may be constructed and arranged to be non-reversible in response to failure of the power means actuating the guide roll and, therefore, holds the roll in position until the condition causing such 'failure can be remedied. Other objects of the invention are to provide a guide follad- Patented Sept. 23, 1958 2 justing means which occuplies a minimum amount of space along the edge of the travelling web, which is sensi-- tive to deviations of the web so as to respond rapidly and without excessive' correction of the guide roll position, andlwhich is economical to construct. and advantages of the invention will become apparent as the disclosure progresses with respect to the accompanying drawings, wherein:

Fig. l is a plan view structure embodying the present invention, with parts broken away.

Fig. 2 is an enlarged fragmentary view of the structure in Fig. l, partly in section.

Fig. 3 is a sectional view taken along the line 3-3 in Fig. 2. 4

Fig. 4 is a plan View of a portion of the structure in Fig. 2, showing another position of some of the parts.

Fig. 5 is a sectional View taken along the line 5 5 in Fig. 4.

Fig. 6 is another plan view similar to Fig. 4 but showing another position for certain portions of the structure.

Fig. 7 is a sectional view taken along the line 7--7 in Fig. 6.

Figs. 8-11 are cross-sectional views of four modifications of the apparatus illustrated in the previous gures.

With reference first to Fig. l of the drawings, it is seen that apparatus chosen to illustrate the present invention comprises generally a guide roll 10 which is disposed in transverse underlying relation to a travelling web 12 in supporting engagement with the latter. The guide roll 10 includes a supporting shaft 14 which extends beyond each end of the roll and is journalled in a pair of bearings 16 and 18.

The bearing 16 is suitably supported on an underlying frame member 20 for pivotal movement about a vertical axis. The bearing 18 at the other end of the guide roll is slidable along the shaft 14 and is pivotally supported on a movable arm 22 for movement about an axis indicated at 23 (Fig. 2), in order to provide for movement of the adjacent end of the roll in the direction of travel of the web 12. This shifting movement of the guide roll axis relative to the direction of travel of the web is utilized to realign the web in the event that it deviates laterally from its normal course.

To produce a shifting of the bearing 18 and thereby angularly adjust the position of the guide roll axis an amount sufficient to compensate for a given web deviation, there is provided mechanism including a detector or feeler 24, and la Huid motor 26 which carries the support arm 22 for the shiftable guide roll bearing 18. The detector 24 is preferably a curved surface plate or the like which affords a of resistance to the normal travel of the web and is suitably mounted for lateral movement in unison with the web, as the latter deviates from its normal course. The iluid motor 26, which is vertically mounted on a frame member 28, carries the bearing 4supportarm 22 and is operatively connected with the feeler 24 in a manner such that movement of the latter controls the operation of the fluid motor to shift the bearing 18 and thereby angularly shift the axis of the guide roll 10.

As seen particularly in Figs. 2 and 3, the fluid motor 26 comprises a vertically disposed cylindrical member 30, which includes a top closure 32 and a bottom closure 34, with the latter being suitably xed to the frame member 28 adjacent the shiftable end of the guide roll. A free piston 36 is slidably disposed within the cylinder 30 and the latter is entirely enclosed by a concentric cylindrical housing 38 which is` mounted on the bottom closure member 34 for rotation relative to the cylinder 30. Aligned openings through the top 32 of the cylinder 30 Iand the top of therotatable housing 38 provide a passageway d0 affording iluid communication between Further objects the upper portion of the cylinder 30 and a source of pressure iiuid to be described later. At the lower end of the cylinder 30 there is provided a similar passage 42 which extends through the bottom plate 34 and the supporting frame member 28. The ends of the lside wall of the piston 36 are suitably sealed, as by O-rings 43, to prevent the seepage of fluid therepast.

Movement of the piston 36 within the cylindrical-member 30 is utilized to provide for rotation of the housing 38 and the arm 22 attached thereto, through means including a pair of grooves 44 and, 46 Vformed on the outer wall of the piston. These grooves are inclined in opposite directions with respect to the axis of the piston and provide a pair of cam surfaces which are disposed for engagement by a pair of followers 48 and 50 which extend into the cylinder 30.

The follower 48 is yrotatably mounted on the end of a pin 52, which is fixed in a complementary opening 54 in the side wall of cylinder 30 at a position mid-way of the depth of the cylinder. The follower 50 is rotatably mounted on the inner end of a pin or stud 56, which extends lthrough a transversely slotted opening 58 in the side of cylinder 30, generally opposite the position of the follower 48, and is secured in a bore 60 in the rotatable housing 38. Consequently, as the piston 36 moves up and down in the cylinder 30, the cam grooves 44 and 46 coact with the followers 48 fand 50, respectively, to produce a limited rotation of the piston as well as a horizontal swinging movement of the follower l50 across the slot 58. Since the follower pin 56 is fixed to the rotatable housing 38, the movement of the pin through the transverse slot 58 is translated into a rotary movement of the housing 38 and the bearing support arm 22 which is attached thereto.

It is seen, therefore, that movement of the bearing 18, which is mounted on the arm 22 and supports one end of the guide roll 10, is controlled through movement of the piston 36 of the fluid motor 26. Furthermore, as seen particularly in Figs. 4-7, the grooves 44 and 46 in the piston, as well as the transverse slot 58 in the wall of the cylinder 30, are preferably designed to provide substantially more movement of the arm 22 than isfordinarily required in adjusting the position of the guide roll 10. In the illustrated example the slot 58 accommodates approximately 70 movement of the follower pin 56, with the cam groove 44 affording about 35 rotation of the piston 36 and the cam groove 46 providing an additional 35 movement of the follower 50. In this respect it should be noted that the grooves 44 and 46 in Figs. 5 andi-7 have been distorted and exaggerated with respect lto the showings in Figs. 4 land 6, in order to present aclear illustration of the structure in each instance in.a. single cross-sectional view.

The described anvles' of the grooves 44 land 46 and the slot S8 aremore. than ample for most purposes, without interfering with properV operation of the cam followers 48 and and 50 at the ends of the piston stroke, but m-ay be varied as desired. With the motor 26 normally operating intermediate its limit position, thepiston 36 is always subjected to fluid pressure on both-ends and, in this way, more precise controlV of the position of the piston is afforded. Thus there is provided a very accurate positioning of the bearing support `armi22 by a means which is readily responsive to any deviation of the web.

It will be seen, therefore, that the primary purpose of thegroove 44, which is engagedby the stationery follower 48, is. to increase. the field of movement of the oppositely disposed pin 56, by effecting a rotation of the piston .36 as it moves up and down in the cylinder 30. Adequate movement of the follower 50 and the rotatable housing 38, latlixed thereto can be afforded in many in stances without rotation of the. piston, as in the modifications illustrated in Figs. 8, 9 and l1 to be described hereinafter.

It should also bexnoted that the relationship of the slot 44 to the slot 46 (Figs. 3-5) may be varied to achieve any particularly desired result. That is, these slots may be disposed at different angles which are selected to achieve a predetermined amount of rotation of the piston 36 and a selected range of movement of the rotatable housing 38.

Looking particularly at Fig. 2, it is seen that fluid .communication with the passages 40 and 42 yat opposite ends of the cylinder 30 is provided by a pair of pipes cr tubes 62 and 64, respectively, which are connected with a control valve housing 66 mounted on one side of the fiuid motor housing 38. The housing 66 in turn communicates with a suitable source of pressure fluid, such as the pump indicated. generally at 67, through a pair of conduits 68 and 70 which provide for the flow of pressure fluid to the housing 66 and the return flow to the reservoir portion of the pump.

The housing 66 contains a four-way, slidable spool valve 72 which includes three spaced apart sections 74,

2) by a spring 94 interposed between one end of; the` valve and the end of the valve housing 66. Preferably the end of the valve housing containing the spring94 includes a detachable closure member 96 havingjan internally threaded end portion which is engageable with an externally threaded end portion of the housing. ln this way access to the valve 72 is provided and, also, the disposition of the spring 94 isv easily `adjusted by turning the closure member 96.

The end of the valve 72 opposite that which bears against the spring 94 extends through the housing 66 to present a post 98 which is connected through suitable linkage with the feeler 24. More particularly, the feeler assembly 24 is supported by an arm 100 which is carried by the fiuid motor 26 in fixed relation to the stationary cylinder 30 (Fig. 2). The outer end of arm 100 includes a split sleeve element 102 which is disposed to adjustably receive one end of an elongated rod 104 extending toward the web 12 and at generally right angles to the direction of travel of the web. The inner end of the rod 104 overlies the adjacent edge portion of the travelling web and has suitably secured thereto a bracket 106.

The bracket 106 is adjustably fixed to the rod.104, as by a nut 103 disposed through a bifurcated portion of the bracket which clamps on to the rod 104, and extends generally parallel to the direction of travel of the web 12. The free end of the bracket 106 has mounted thereon a pivot `bearing means 110, rotatably supporting a depending stub shaft 112. The lower end of the stub shaft has suitably fixed thereto a palm arm 114 which extends along the edge of the web and carries the palm portion 116 of the feeler assembly 24 at its outer end. intermediate the ends of the palm arm 114 there is provided an adjustable linkage connection with the control valve 72 which regulates the movement of the fluid motor 26. More specifically, a pair of rods 118 and 120 are disposed in extension forming relation to one another by a suitable coupling element 122. Theend of the rod 118 adjacent the palm arm 114 is pivotally secured thereto by a bracket 124 adjustably positioned along the arm. The opposite end of the other rod 120 is pivotally connected to the end of the post 98 on the valve 72, as by a ball and socket bearing joint 126.

Consequently, the linkage intermediate the palm arm 114 and the valve spool 72 is free to swing relative to each of these attached parts, to thereby accommodate the swinging movement of the palm arm 114 as well as the rotation of the outer housing 38 of the fluid motor 26. Furthermore, it is seen that the spring 94 in the valve housing 66 constantly urges the palm 116 into engagement with the edge of the web 12, and that any lateral shifting of the web is transmitted through the linkage just describedl to the valve 72. The valve 72 then provides a corresponding motion of the fluid motor 26 to shift the position of the guide roll 10.

Assuming that the web 12 is travelling in its intended course, the bearings 16 and 18 are then disposed in axial alignment so as to position the guide roll at right angles to the direction of web travel, and the fluid motor 26 is in its neutral position shown in Figs. 2 and 3. A deviation of the web to the right, as viewed in Fig. 1, creates a pressure against the feeler 24 which in turn operates through the linkage connection with control valve 72 to move the latter inwardly of the housing, that is downwardly in Fig. 2.

The control valve section 82 is thus moved to provide uid communication between the pressure iluid inlet 84 and the passage 90, around the reduced section 76, to cause a flow of pressure fluid through the passage 62 to the -upper side of the piston 36. At the same time, the valve section 80 is moved to provide communication between the passage 92 and the return flow passage 86, around the reduced section 74, to thereby permit fluid to drain from the lower side of the piston through the conduit 64 and the control valve housing 66 and thus return to the source.

The above movement of pressure fluid forces the piston l the arm 22 are, therefore, rotated clockwise to thereby shift the bearing 18 and the associated end of the guide roll 10 in the direction of travel of the web 12, that is, to the right as seen in Fig. 2. This axial' shifting of the guide roll produced a non-uniform drag on the web which causes the latter to move to the left (Fig. l) toward its normal course.

Sucient shifting of the web to the left will of course permit the feeler 24 to follow such movement and return the control valve to its neutral position or, if the web goes beyond its normal course, it will be followed by the feeler 24 which will then cause the control valve 72 to move outwardly of the housing 66 (upwardly in Fig. 2). The pressure fluid will then be directed to move the piston 36 upwardly (Fig. 5) and thereby shift the bearing 18 in the opposite direction, or to the -left in Fig. 2.

The latter action is, of course, a hunting effect which is undesirable. This effect is largely eliminated by the novel disposition of the control valve on the rotatable housing 38. As a result of this arrangement, the end 98 of control valve 72 is not only movable in response to movement of the feeler 24 but, also, moves in an arcuate-like path, as indicated by the positions A and B in Fig. 2, as the iluid motor housing 38 rotates to shift the guide roll axis. Consequently, in the above described operation wherein the control valve 72 moves inwardly of the housing and produces a clockwise rotation of the housing 38, the latter rotation causes the valve housing 66 to move away from the Valve 72, i. e. downwardly in Fig. 2. This causes the valve 72 to move outwardly of the housing 66, whereupon Valve section 82 will close off passage 90 to prevent further clockwise rotation of the fluid motor housing.

The disposition of the valve housing 66 and the arrangement of the linkage betweenl the control valve and i the feeler 24 is such that the return of the valve to its neutral position, to thereby shut off the How of pressure iluid to the motor 26, occurs after a predetermined amount of rotation of the housing 38 within which movement proper compensation for the web deviation has been effected. This automatic shut-off feature is importam in eliminating hunting of the guide `roll con `keyed thereto to prevent rotation of the piston.

trol which is common `with installations wherein the control valves are disposed in stationary housings.

Another very important advantage afforded by the described arrangement is that it provides stability for the `guide roll in the event of fluid pressure failure. That is, in the event the iluid pressure exerted on the piston 36 should fail, the piston is not readily susceptible to movement by virtue of the force exerted by the travelling web on the guide roll 10, which force tends to swing the guide roll about the fixed pivot mounting 16 and which is transmitted through the bearing 18, arm 22, housing 38, and the follower 50 to the piston 36. The disposition of the groove 46, as well asthe groove 44, is such that a considerable force is required to be exerted through the follower 50 in order to move the piston 36 and thereby permit a shift of the guide roll, as compared with the force required on the end of the piston to elfect a shifting of the follower and a resulting movement of the guide roll 10. This diierence in mechanical advantage is sucient to resist the tendency of the guide roll to swing about the pivot 16 when the pressure in the iiuid motor 26 fails, without detracting from the sensitivity of the guide roll control and its ability to readily correct the position of the guide roll during ordinary operation.

It will be apparent that the angular disposition of the grooves 44 and 46 is a great factor in determining whether or not the piston 36 can be reversed through the force of the guide roll 1G when pressure in the fluid motor 26 fails. The greater the angle between the path defined by the slot S8 and the direction of the grooves 44 and 46 the more diicult it will be for action of the guide roll to move the piston 36. In most guide roll installations the required sweep of the guide roll is not very great and, consequently, rather sharp inclines of the grooves 44 and 46 will afford the desired range of guide roll movement. For example, in most instances a total sweep of 'Ofa for the guide roll would aord adequate control of the web deviations encountered. To provide a sweep of 60 in the structure of Figs. l'7, each of the grooves 44 and 46 need be disposed at an angle of only 15 with respect to a vertical line through the midpoint of the length of the grooves. This arrangement provides 30 rotary movement of the piston 36 with respect to each of its followers 48 and 50 for a total of 60.

It will also be recognized that the above described feature of construction which prevents movement of the piston 36 when the fluid pressure in the cylinder 30 fails, is particularly important when the guide roll is disposed in other than a horizontal plane. In such case there is present not only the drag of the web on the guide roll but also the gravitational effect on the guide roll, which produce a force on the follower 50 tending to move the piston 36.

It should further be recognized that various modifications of the described structure can be made without departing from the principles of this invention. For example, in Fig. 8 there i's shown an arrangement for the uid motor 26 wherein no rotation of the piston is provided. In this instance the piston includes a curved groove 132 and a follower 134 extending through a radial slot in the cylinder 30 in the manner shown in Fig. 3. However, the piston also includes a straight vertical slot 136 receiving a follower 138 which is xed to the cylinder 30 and thus rotation of the piston is prevented.

In Fig. 9 is shown a fluid motor arrangement wherein the piston 140 is slidably mounted on a rod 142 and A follower 144 is fixed -to the piston and extends into a curved groove 146 disposed along the inside Wall of a rotatable "cylinder 148 and the `rod 142 extends through both of these parts and is lixedly secured tothe outer housing. Fluid pressure meanscommunieates with therinterior of the cylinder 148 through .a pair of conduits 152 and 154. An arm 156 is `fixed -to the rotatable cylinder to provide means for connection with the shiftableguide.- Consequently, as the'piston 140 is movedy roll bearing. along the rod 142, the follower 144 moves through the curved groove 146 to effect a rotation of the cylinder 148 and the arm 156 to thereby shift the guide roll.

Another embodimentA shown in Fig. l depicts the use of a single groove 158 in a free piston 16), wherein a reverse curve is kformed by the groove and a pair of followers 162 and 164 are both disposed within the single groove. The follower 162 is fixed in the stationary cylindrical member 166 and provides a guide` for determining the amount of rotation of the piston 160. The other follower 164 extends through a radial slot 168 in the cylinder 166 and is secured to the rotatable housing 170. A suitable bracket 172 which is secured to the housing 170 provides means for connection with the guide roll to shift the latter as thehousing is rotatedy by vertical movement of the piston 160. As the piston is moved through the introduction of pressure fluid into the cylinder 166, the follower 162 affords a controlled rotation of the piston and this rotation plus the vertical movement of piston 160 is translated, through the 4force exerted by the upper follower 164, into rotation of the housing 170.

In Fig. ll is shown still another modified form of fluid motor which may be used with the apparatus shown in Figs. l and 2. In this embodiment there is provided a stationary housing 174 which fixedly supports a center rod 176 having a piston 178 non-rotatably and axially secured thereto by means including a key 180. The piston is enclosed by a relatively movable cylindrical member 182 having iiuid communication with a source of pressure fluid through a pair of conduits 184 and 186 which are disposed at opposite ends of the chamber.

The outer wall surface of the cylindrical member 182 includes a pair of grooves 188 and 190 which receive a pair of follower elements 192 and 194, respectively, The follower 192 is secured in position on the housing 174 and, consequently, defines the extent of rotation afforded for 'the cylinder 182 in a manner similar to that described with respect to the previous embodiments. Thel groove 188 may be curved or, if no rotation of the cylinder 182 is desired, the groove 188 can be made parallel to the axis of the rod 176. The follower 194 is secured to a rotatable structure 196 having connection with the guide roll through means including an arm 198.

The follower 194 extends into the groove 190 which is suitably curved so that, as the cylinder 182 moves along the wall of the piston 178, a force is transmitted through the follower 194 to effect a rotation of the structure 196 and a corresponding shifting of the guide roll. In order to provide room for the fluid pressure conduits 184 and 186 it is preferred that the structure 196 be in the form of a partial cylinder. The housing 174 may be in any suitable form such as an angle bracket or a partial cylinder which is complementary to the casing 196 and forms therewith a complete enclosure for the cylinder. 182;

The foregoing are intended only to illustrate some of the possible modifications of the preferred structure in Figs. 1-7, and it should be apparent that other modifications might readily be made without departing from the principles of the present invention.

It is seen from the foregoing, therefore, that apparatus constructed in accordance with this invention provides an improved means for controlling the position of a guide roll, wherein movement of a piston through a path generally normal to the plane of the travelling web is effective to shift the guide roll inthe direction of movement of the web. This arrangement provides a more positive and precise control of the guide roll in a manner affording a considerable saving in the space required for the guide roll control unit.

And, as indicated above, another important advantage offered by this invention is that it provides for a constructionfwhich does not afford free movement of the guide roll in the event of failure of the pressure fluid in the control system. The particular arrangement of parts holds the operating piston in position when such failure occurs and thereby avoids possible damage to the travelling web. It is also seen that the arrangement of the control valve for the fluid motor is such that an automatic shut-off is provided for the fluid'pressure at the ends of a predetermined range of movement of the fluid motor. T his is very effective in minimizing the tendency of the guide roll to overcorrect and thus continually hunt for the normal path of the travelling web.

Although shown and described with respect to particular apparatus and in connection with a horizontally moving web, it will be readily apparent to those skilled in the art that the principles of the present invention may also be applied in connection with other apparatus and to travelling webs disposed in a plane other than horizontal.

I claim:

l. In combination with a guide roll mounted on a cross shaft for movement relative to a travelling web being guided thereby, adjusting means for effecting movement of .said guide roll comprising a cylindrical housing, a piston disposed within said housing for relative axial movement therebetween, said adjusting means also including means affording guided relative rotation between said piston and cylindrical housing in response to relative axial movement therebetween, uid pressure means communicatingwith opposite ends of said piston and operable to produce said relative axial movement, said fluid pressure means including a control valve housing :mounted for rotation about the axis of said piston along with said relative rotation between said piston and cylindrical housing, andy a control valve movably positioned in said `control valve.

housing to direct the ow of pressure fluid relativetosaid piston, means associated with said control valve 4anid. op-

erable in response to deviating movement of the travelling, web to alter the position ofsaid control valve relative :to 1

said control valve housing, and means connecting said adjusting means with said cross-shaft so that said relative rotation .of said piston and cylindrical housing is effective toA produce a shifting of saidcross-shaft with respect to the direction of travel of the web.

2. In combination with a guide roll mounted on a crossshaft for movement relative to a travelling web being,

guided thereby, means for effecting movement of said guide roll comprising a cylindrical housing mounted adjacent one end of said guide roll for rotation about an axis which is generally normal to the travelling web, a bearing support for one end of said guide roll fixed to said cylindrical housing for rotation therewith, a piston slidably disposed within said housing for movement relative thereto, means connecting said piston with said cylindrical housing so that axial movement of said piston relative to said housing causes the latter to rotate, fluid pressure means communicating with said cylindrical housing and operable to produce movement of said piston, said uid pressure means including a control valve mounted on said rotatable housing which is operable to selectively direct the flow of pressure fluid relative to said piston housing, a feeler means engaging the edge of said travelling web and mounted for movement in response to lateral shifting movement of the web, means connecting said feeler means with said control valve for operation of the latter in response to lateral shifting of the web, said connecting means being also operative to respond to the rotation of said control valve with said rotatable housing to return said control valve to its neutral position after a predetermined amount of movement of said valve with said hous- 3. A guide for a travelling web comprising a guide roll engageable with said web, means supporting said guide roll in a manner affording swinging movement thereof about an axis normal to said web, a feeler means mounted for engagement with an edge of said web and movable in response to lateral shifting of the web, and guide roll control means operable to effect a swinging movement of said guide roll in response to movement of said feeler means, said guide roll control means including a hydraulic motor comprising a cylindrical housing rotatably mounted on a fixed cylindrical member in concentric relation thereto with the axis of said cylindrical member and housing being disposed generally normal to the path of the travelling web, a piston slidably disposed within said cylindrical member, said piston including a pair -of recesses formed along its outer Wall in spaced relation to each other and disposed in generally oppositely inclined relation to the direction of travel of the piston, a first follower fixed to said cylindrical member and disposedwithin one of the recesses in said piston, means defining a transverse slot in said cylindri-cal member, a second follower fixed to said cylindrical housing and extending through said transverse slot to a position within the other of said recesses in said piston, means for selectively supplying pressure fluid to opposite ends of said piston, whereby axial movement of said piston is accompanied by a rotation of said piston within the limits defined by said first follower and said one recess and by a movement of said second follower across said transverse slot to effect a rotation of said cylindrical housing, said means for supplying pressure fluid being connected with said feeler means for operation in response to movement of said feeler means, and means connecting said rotatable cylindrical housing with the support means for said guide roll.

4. In combination with a guide roll mounted on a crossshaft for movement relative to a travelling web being guided thereby, means for effecting mnvement of said guide roll comprising a cylindrical housing having its axis disposed substantially normal to the path of the travelling web, a piston disposed within said housing for guided movement relative thereto, said piston including an elongated groove formed in the surface thereof and extending therealong at an angle with respect to the central axis of said piston, a follower disposed in said groove and extending outwardly therefrom through a radial slot in said cylindrical housing, means connecting said follower with said cross-shaft, fluid pressure means communicating with opposite ends of said piston and operable to produce said axial movement of said piston, whereby said groove and follower coact to provide rotation of the piston as said piston moves axially of said cylindrical housing to thereby afford movement of said cross-shaft, said groove and follower being thereby constructed and arranged with respect to said cylindrical housing to provide sufficient resistance to the force exerted by said cross-shaft, due to its frictional engagement with said travelling web, so as to prevent an axial shiftin the position of said piston in response to the failure of the uid pressure within said cylindrical housing.

5. In combination with a guide roll mounted for movement relative to a travelling web being guided thereby, means for effecting movement of said guide roll comprising a cylindrical housing disposed with its longitudinal axis generally normal to the travelling web, a piston disposed within said housing for sliding movement relative thereto, said piston including a groove formed along its outer wall in angularly extending relation to the axis of said piston, a pair of spaced apart follower elements disposed within said groove, one of said follower elements being fixed to said housing, the other of said follower elements extending through a radial slot through said cylindrical housing, means connecting said other follower element with said cross-shaft, and fluid pressure means communicating with opposite ends of said piston, whereby axial movement of said piston in response to said fluid 10 pressure also affords a rotation of said piston which is transmitted through said other follower element to said cross shaft so as to effect a corresponding shifting thereof.

6. In combination with a guide roll mounted for swinging movement relative to a travelling web being guided thereby, means for effecting movement of said guide roll comprising a fixed piston having its axis generally normal to the path ofthe travelling web, a cylindrical member enclosing said piston and movable relative thereto, fluid pressure means communicating with said cylindrical member and operable to afford axial movement of said cylindrical member relative to said piston, said cylindrical member including a pair of grooves formed along its outer wall surface in obliquely extending relation to the axis of said member, a first follower element fixedly disposed in position for engagement with one of said grooves to thereby afford limited rotation of said member as it is moved axially of said piston, rotatable means disposed adjacent to the other of said grooves in said member and supported for circumferential movement about the axis of said piston, a second follower element secured to said rotatable means in position for engagement with said said other groove, and additional means affording a connection between said rotatable means and said guide roll, whereby axial movement of said cylindrical member affords a rotation of said rotatable means through the coaction of said other groove with said second follower element and whereby said rotation effects a corresponding movement of said guide roll.

7. In combination with a guide roll mounted on a cross-shaft for movement relative to a travelling web being guided thereby, means for effecting movement of said guide roll comprising a cylindrical housing having its axis disposed substantially normal to the path of the travelling web, a piston disposed within said housing for movement relative thereto, said piston including a pair of recesses formed along the outer wall thereof, one of said recesses extending in generally parallel relation to the center axis of said piston, a first follower fixed to said cylindrical housing and disposed within said one recess in said piston, the other of said recesses being disposed in inclined relation with respect to the center axis of said piston, means defining a transverse slot in said cylindrical housing, a second follower disposed within said other recess in said piston and extending outwardly therefrom through the transverse slot in said cylindrical housing, means connecting said second follower with said said cross-shaft, and means affording pressure fluid communication with opposite ends of said cylindrical housing, whereby movement of said piston causes said second follower to move across said transverse slot and move said cross-shaft.

8. In combination with a guide roll mounted on a cross-shaft for movement relative to a travelling web being guided thereby, means for effecting movement of said guide roll comprising a cylindrical housing having its axis disposed substantially normal to the path of the travelling web, a rod disposed axially of said housing, a piston slidable within said cylindrical housing and carried by said rod for axial movement therealong, said cylindrical housing including a recess formed along the inner wall thereof and disposed in inclined relation to the direction of travel of said piston, a follower fixed to said piston and disposed within said recess formed in the inner wall of said housing, means connecting said cylindrical housing with said cross-shaft, and means affording pressure fluid communication with opposite ends of said cylindrical housing, whereby movement of said piston causes said follower to move in said,` recess formed in the housing inner wall to thereby rotate said housing and effect an adjustment of the position of said cross-shaft.

9. A guide for a travelling web comprising a guide roll engageable with said web, means supporting said guide roll in a manner affording swinging movement thereof about an axis normal to said web, a feeler means mounted for engagement with an edge of said web and movable in response to lateral shifting of said web, and guide roll control means operable to effect a swinging movement of said guide roll in response to movement of said feeler means, said guide roll control means including a hydraulic motor comprising a cylindrical housing rotatably mounted on a fixed cylindrical member in concentric relation thereto, with the axis of said cylindrical member and housing being disposed generally normal to the path of the travelling web, a piston slidably disposed within said cylindrical member, said piston including a pair of recesses formed along its outer wall in spaced relation to each other and disposed in generally oppositely inclined relation to the direction of travel of the piston, a first follower fixed to said cylindrical member and disposed within one of the recesses in said piston, means defining a transverse slot in said cylindrical member, a second follower fixed to said cylindrical housing and extending through said transverse slot to a position within the other of said recesses in said piston, means for selectively supplying `a pressure fiuid to opposite ends of said piston including a control valve which is mounted on said rotatable housing and which is operable to direct the flow of pressure fluid relative to said cylindrical member, said control valve being connected with said feeler means for operation in response to movement of said feeler means, whereby axial movement of said piston is accompanied by a rotation of said piston within the limits defined by said first follower and said one recess and by a movement of` said second follower across said transverse slot to effect a rotation of said cylindrical housing, said connection between .said feeler means and said control valve being also operative to respond to the rotation of said control valve with said rotatable housing to return said control Valve to its neutral position after a predetermined amount of movement of said valve with said housing.

10. In combination with a guide roll mounted on a cross-shaft for movement relative to a travelling web being guided thereby, means for effecting movement of said guide roll comprising a cylindrical housing having its axis disposed substantially normal to the path ofthe travelling web, a piston disposed within said housing for movement relative thereto, said piston including a pair of recesses formed along the outer wall thereof and disposed in generally oppositely inclined relation with respect to the direction of travel of said piston, a first follower fixed to said cylindrical housing anddisposed within one of the recesses formed in said piston, means defining a transverse slot in said cylindrical housing, a second follower disposed within the other of the recesses formed in said piston and extending outwardly therefrom through the transverse slot in said cylindrical housing, means connecting said second follower with said crossshaft, and means affording pressure fluid communication with opposite ends of said cylindrical housing whereby movement of said piston causes said second follower to move across said transverse slot and move said crossshaft, and whereby the oppositely inclined relation of the recesses in said piston is effective to provide a rotation of said second follower which is the sum of the amounts of rotation afforded by each recess in said piston.

11. A 'fiuid motor comprising a cylindrical housing rotatablymounted on a fixed cylindrical member in concentric relation thereto, a piston slidably disposed within said cylindrical member, said piston including a groove formed along its outer wall in angularly extending relation to the axis of said piston with one portion of said groove extending at an angle with respect to another portion of said groove, a pair of spaced apart follower elements disposed within said groove, one of said follower elements extending through a transverse slot in said'cylindrical member and connected with said rotatable housing, the other of said follower elements being fixed to said cylindrical member, and means affording pressure fluid communication with opposite ends of said cylindrical member, whereby axial movement of said piston causes said one follower to move across said transw verse slot and rotate said cylindrical housing.

l2. A fiuid motor comprising a fixed piston, a cylindrical member enclosing said piston and movable relative thereto, means affording pressure fluid communication with opposite ends of said cylindrical member to thereby provide for axial movement of said member relative to said piston, said cylindrical member including a pair of grooves formed along its outer wall surface in obliquely extending relation to the axis of said member, a first follower element fixedly disposed in position for engagement with one of said grooves to thereby afford limited rotation of said cylinder member as it is moved axially of said piston, rotatable means disposed adjacent to the other of said grooves in said member and supported for movement about the axis of said piston, a second follower element secured to said rotatable means in position for'engagement with said other groove, whereby axial movement of said cylindrical member affords a rotationof said rotatable means.

13. A fluid motor comprising a cylindrical housing rotatably mounted on a fixed cylindrical member in concentric relation thereto, a piston slidably disposed within said cylindrical member, a pair of recesses formed along the outer wall of said piston and disposed in generally oppositely inclined relation to the direction of travel of said piston, a first follower fixed to said cylindrical member. and disposed within one of said recesses in said piston, means defining `a transverse slot in said cylindrical member, a second follower fixed to said cylindrical housing and extending through said transverse slot in said cylindrical member to a position within the other of said recesses in said piston, and means affording pressure fiuid communication with opposite ends of said cylindrical member, whereby movement of said piston causes said second follower to move across said transverse slot and rotate said ,cylindrical housing.

References Cited in the file of this patent UNITED STATES PATENTS 711,139 Warren Oct. 14, 1902 1,066,687 Warren July 8, 1913 1,801,633 MacKirdy Apr. 21, 1931 2,192,175 Ballard Mar. 5, 1940 2,204,649 Barnhardt .Tune 18, 1940 2,632,642 Cooper Mar. 24, 1953 sui- 14.1 

